Cylinder bore wall oil squirter, reciprocating engine embodying same and where the engine further embodies a rollerized cranktrain

ABSTRACT

Featured is a cylinder wall oil delivery system for a reciprocating engine having at least one cylinder and at least one piston movably received in the cylinder as well as a reciprocating engine embodying such a cylinder wall oil delivery system. Such an oil delivery system includes a squirter that is fixably arranged in each cylinder so that oil is directed therefrom to two different areas of the cylinder wall. The squirter includes a first nozzle being orientated so the oil is directed to one of the two cylinder wall areas and a second nozzle being orientated so the oil is directed to the other of two cylinder wall areas. In particular embodiments, the squirter is arranged so the oil targets the piston skirt thrust and anti-thrust travel areas of the cylinder wall and so as to regulate the oil flow from each nozzle.

FIELD OF INVENTION

The present invention generally relates to oil lubrication systems, moreparticularly to oil lubrication systems of a reciprocating engine andyet more particularly to oil lubrication systems of a reciprocatingengine that embodies a rolling bearing element in the cranktrain.

BACKGROUND OF THE INVENTION

As shown in FIG. 1A, many reciprocating engines embody an hydrodynamiccranktrain in which pressurized oil is fed to the crankshaft 10 throughcross-drillings and also is fed to the connecting rod big end plainbearing 15 that is disposed between a surface of the crankshaft and theopposing surface of the big end 13 of the connecting rod 12. In such anengine, the crankshaft 10 is rotatably supported by the main plainbearing 11 secured between the block and the structure (e.g., mainbearing cap) secured to the block. The piston 12 is movably received inthe cylinder 2 and is rotatably coupled to the crankshaft 10 by theconnecting rod 12.

In a hydrodynamic bearing pressurized oil crankshaft, the squeezingaction between the connecting rod 14 and the big end journal, as well asthe amount of side clearance, all combine to provide sufficient oilpressure so that a sufficient oil splash is provided to the cylinderwalls 4 every time the crankshaft throw is in the top dead center (TDC)region. In addition, the connecting rod 14 can be configured so as toinclude a radial hole(s) (e.g., oiling slots 17 as shown in FIG. 1B) atthe connecting rod big end 13 that provides additional cylinder walllubrication via an oil spray. The various oil sprays occurring duringoperation are illustrated in FIG. 1A.

In addition to the above-described conventional technique that providesoil as a lubricant between the cylinder walls 4 and the moving elements(e.g., piston, piston rings), other mechanisms or devices have beendeveloped to cool the piston and/or piston rings such as by directing aspray or jet of oil at the piston. For example, one or more nozzles arearranged within a cylinder of a reciprocating engine and these one ormore nozzles is/are arranged in the cylinder so as to be aimed at theunderside of the piston. In this way, the oil exiting the one or morenozzles impinges on the underneath surfaces of the piston and acts as acoolant oil that cools the piston.

There is found in U.S. Pat. No. 4,206,726 an oil cooling system for apiston. As indicated therein, each piston has a crown, a depending skirtand a ring-receiving groove on the skirt near the crown. On theunderneath side of the piston there is included a central cavityterminating near the crown and coolant receiving means in heat exchangerelation to the groove. Two nozzles are provided and arranged within thecylinder so that a first jet of oil is directed to the piston cavity anda second jet directs the oil to the coolant receiving means of thepiston for all operating positions of the piston within the cylinder. Itis further expressly indicated that means are provided for supplying oilto the nozzles which oil acts as the coolant.

It is further indicated that, in connection with a highly preferred formof the reciprocating engine, one of the nozzles is arranged so that thefirst jet is at an angle with respect to the longitudinal axis of thecylinder, so the oil coolant sweeps along the cavity and avoidsinterference with engine parts. Also, it is indicated that the secondnozzle is arranged so that the second jet is generally parallel to thelongitudinal axis.

There is found in Japanese Publication No. 2008-163936 an internalcombustion engine including a piston that reciprocatingly moves in acylinder of a cylinder block. Such an engine further includes a rearside oil jet 210 that injects oil to a skirt inner region and a skirtouter region of the piston from the side of the piston connecting rod.Thus, this publication describes directing oil as a coolant to theunderside of the piston between the skirts and piston pin.

It should be recognized that these conventional systems are based on areciprocating engine that uses a hydrodynamic bearing pressurized oilcrankshaft. However, when a different bearing system is contemplated(e.g., a rollerized crankshaft for example) for use in suchreciprocating engine, the operating conditions are different and thusthe above described cylinder wall oil delivery system that splashes oilon the cylinder wall will not be effective in providing oil to thecylinder walls.

As indicated above, in conventional reciprocating engine plain bearings11, 15 are used to rotatably support the connecting rod 14 and thecrankshaft 10. In order to improve engine performance, it has beenconsidered to replace the plain bearings 11, 15 with roller element orroller type bearings 21, 25 (FIG. 2). Referring now to FIG. 2 there isshown a cross-sectional side view of a conventional cylinder 2 in whicha piston 12 is movably received and which piston is mechanically coupledto the crankshaft 20 via a connecting rod 24, having a big end 23. Theconnecting rod 24, more particularly the connecting rod big end 23, isrotatably supported off the crankshaft 10 by a roller bearing 15 that isdisposed between a surface of the crankshaft and an opposing surface ofthe connecting rod big end 23. Similarly, the crankshaft 20 is rotatablysupported by another rolling bearing 21 from cylinder block relatedstructure. In the illustrated oil delivery system, an oil mist supplieslube to the connecting rod roller bearing 15 via axial clearance.

In contrast to the oil delivery system described in FIGS. 1A-B, no formof oil spray (or splash) is being provided to the cylinders walls 4, butrather an oil mist (high pressure atomized oil) impinges on the thrustside of the cylinder wall/liner. Moreover, only about ⅓^(rd) of thecylinder bore from BDC gets direct oil mist. As a result, the oil mistregion is not adequate to reach the piston ring region at BDC.

In the lubrication regime shown in FIG. 2, oil mist is the primarysource of lubricant for the piston group/cylinder wall interface. Aconventional cylinder liner for reciprocating engines on the other handis generally intended for use with an oil spray lubrication regime ormethodology. In those cases where an oil mist lubrication regime is theintended methodology for lubrication in a reciprocating engine, thecylinder liners are typically provided with tough coatings (e.g.,Nikasil or Galnikai) along the cylinder walls. Such tough coatings aretypically found on the liners provided or used in 2 stroke engineapplications.

It thus would be desirable to provide a cylinder wall oil deliverysystem that can provide an effective amount of oil to the cylinderwalls, particularly when the reciprocating engine does not embody ahydrodynamic bearing pressurized oil crankshaft. It also would bedesirable to provide a reciprocating engine embodying such a cylinderwall oil delivery system. It would be particularly desirable to providesuch an oil delivery system that would be at least as effective as priorart devices/systems for applying oil to the cylinder walls, and moreparticularly when the reciprocating engine has a rollerized cranktrain.

SUMMARY OF THE INVENTION

The present invention features a cylinder wall oil delivery system for areciprocating engine having at least one cylinder and at least onepiston movably received in the cylinder. Also featured is reciprocatingengine that embodies such a cylinder wall oil delivery system. Such anoil delivery system includes a squirter that is fixably arranged in eachof at least one cylinder of a reciprocating engine so that oil isdirected therefrom to two different areas of the cylinder wall. Inparticular embodiments, the squirter includes a first nozzle that isorientated so the oil is directed to one of the two cylinder wall areasand the second nozzle is orientated so the oil is directed to the otherof two cylinder wall areas. In more particular embodiments, the squirteris arranged so as to regulate the oil flow from each nozzle.

In yet more particular embodiments, the squirter is arranged in thecylinder so that the oil spray/jet targets a region of the cylinder wallcorresponding to piston skirt thrust and anti-thrust travel areas.

In yet more particular embodiments, the squirter includes a sub-assemblyincluding a first member and a second member that are joined together soas to form the first and second nozzles. Also, the first and secondmembers are configured so as to regulate the flow from each nozzle. Infurther embodiments, the first and second members are further configuredso that the flow from each nozzle lies within a range of desired valuesor so the flow from each nozzle is about the same.

In yet further embodiments, the cylinder wall oil delivery systemfurther includes a pressure regulator operably coupled to the squirterso that oil is delivered to the squirter when pressure of the oilexceeds a predetermined value.

According to another aspect of the present invention there is featured areciprocating engine including a block having at least one cylindertherein, at least one piston, each piston being movably received in acorresponding cylinder, and a squirter that is fixably arranged in eachof the at least one cylinder so that oil is directed therefrom to twodifferent areas of the cylinder wall. Such a squirter includes a firstnozzle that is orientated so that oil is directed therefrom to one ofthe two areas of the cylinder wall and the second nozzle is orientatedso that oil is directed therefrom to the other of the two areas of thecylinder wall.

In yet further embodiments, the squirter is arranged in the cylinder sothe oil spray/jet targets a region of the cylinder wall corresponding topiston skirt thrust and anti-thrust travel areas.

In yet further embodiments, the squirter includes a sub-assemblyincluding a first member and a second member that are joined together soas to form the first and second nozzles. Also, the first and secondmembers are configured so as to regulate the flow from each nozzle.Further, the first and second members are further configured so that theflow from each nozzle lies within a range of desired values or so theflow from each nozzle is about the same.

In yet further embodiments, the reciprocating engine further includes apressure regulator operably coupled to the squirter so that oil isdelivered to the squirter when pressure of the oil exceeds apredetermined value.

In yet further embodiments, the block of such a reciprocating engine isconfigured so as to include 4 cylinders, 6 cylinders, 8 cylinders, 10cylinders and 12 cylinders, and where the number of pistons correspondsto the number of cylinders. Such cylinders are arranged in thereciprocating engine so as to be in a line, slanted, form a V, orarranged in any of a number of ways as one known to those skilled in theart.

In yet further embodiments, the reciprocating engine is a four-strokeinternal combustion engine or a two-stroke internal combustion engine.

In yet further embodiments, the reciprocating engine further includes acrankshaft and at least one connecting rod operably coupled to said atleast one piston and the crankshaft such that linear motion of the atleast one piston in the at least one cylinder causes rotation of thecrankshaft. Such a reciprocating engine also further includes a rollingelement bearing that rotatably supports the crankshaft during operationof the reciprocating engine.

In yet further aspects/embodiments of the present invention the oil fromsuch a squirter provides cooling by oil spray wash-up. Also, oilwash-down of the oil sprayed from the squirter further causes lubricantto be splashed onto the connecting rod bearings. Other aspects andembodiments of the invention are discussed below.

DEFINITIONS

The instant invention is most clearly understood with reference to thefollowing definitions:

As used in the specification and claims, the singular form “a”, “an” and“the” include plural references unless the context clearly dictatesotherwise.

As used herein, the term “comprising” or “including” is intended to meanthat the compositions, methods, devices, apparatuses and systems includethe recited elements, but do not exclude other elements. “Consistingessentially of”, when used to define compositions, devices, apparatuses,systems, and methods, shall mean excluding other elements of anyessential significance to the combination. Embodiments defined by eachof these transition terms are within the scope of this invention.

USP shall be understood to mean U.S. patent Number, namely a U.S. patentgranted by the U.S. Patent and Trademark Office.

TDC shall be understood to mean top dead center and relates to aspecific location or position of the piston within the cylinder as itmoves linearly within the cylinder.

BDC shall be understood to mean bottom dead center and relates to aspecific location or position of the piston within the cylinder as itmoves linearly within the cylinder.

BRIEF DESCRIPTION OF THE DRAWING

For a fuller understanding of the nature and desired objects of thepresent invention, reference is made to the following detaileddescription taken in conjunction with the accompanying drawing figureswherein like reference character denote corresponding parts throughoutthe several views and wherein:

FIG. 1A is an illustrative cross-sectional side view of a cylinder for aconventional reciprocating engine having a conventional hydrodynamicbearing pressurized oil crankshaft.

FIG. 1B is a side view of a the lower end of a conventional connectingrod of FIG. 1A showing the radial oiling slots.

FIG. 2 is an illustrative view of a cylinder having a rollerized cranktrain but utilizing conventional techniques for lubricating the cylinderwalls.

FIG. 3 is a cross-sectional side view of a cylinder for a reciprocatingengine illustrating a cylinder wall oil delivery system according to thepresent invention.

FIG. 4 is a bottom view of the cylinder of FIG. 3, but with theconnecting rod and crankshaft removed for clarity.

FIG. 5 is a cross-sectional side view of the oil squirter of the presentinvention when configured for a non-regulated oil pressure application.

FIG. 6 is a cross-sectional side view of the oil squirter of the presentinvention when configured for a pressure regulated application.

FIG. 7 is an enlarged view of the nozzle end portion of the squirter ofFIGS. 5-6.

FIG. 8 is a schematic view of an alternative fluid delivery subassemblyfor an oil squirter according to another embodiment of the presentinvention.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring now to the various figures of the drawing wherein likereference characters refer to like parts, there is shown in FIG. 3 across-sectional side view of a cylinder 2 for a reciprocating engine 1and showing a cylinder wall oil delivery system 100 according to thepresent invention. Reference also should be made to FIG. 4, which is anupward looking view of the bottom of the cylinder 2 of FIG. 3, but withthe connecting rod and crankshaft removed for clarity.

As shown in FIG. 3, the reciprocating engine 100 includes a cylinderblock 102 in which is disposed one or more cylinder bores or cylinders104, each cylinder having a wall 106. A piston 110 is movably receivedin the cylinder 104 and is rotatably coupled to the crankshaft 120 by aconnecting rod 112 at the big end 114 of the connecting rod. A rollerbearing 116 (connecting rod big end roller bearing) is provided forrotatable support of the connecting rod by the crankshaft (such as shownin FIG. 2) and another roller bearing, a main roller bearing 122 isprovided for rotating support of the crankshaft 120.

In further embodiments, such a roller bearing 116, 122 or rollingelement bearing is any of a number of roller element bearings known tothose skilled in the art and appropriate for the intended use. Inexemplary embodiments, the roller bearings 116, 122 embody amultiplicity of needle bearings or needle bearing elements that arearranged so as to be disposed about an outer surface of the crankshaft120 and so as to be between an inner surface of the connecting rod bigend 114 and the crankshaft outer surface. Such a needle type of rollerbearing further includes other structure (e.g., race) that is configuredso as to prevent axial movement of the needle bearing elements wheninstalled without interfering with the rotational movement. Thisarrangement of roller bearings in combination with the crankshaft isreferred to herein for simplicity as a rollerized crankshaft.

Such roller bearing do not require and/or do not support high volumes ofpressurized oil as would be required for the hydrodynamic bearings usedwith a conventional crankshaft. As a consequence of this reduced needfor pressurized oil, in the present invention the cylinder block oilfeeds to the crankshaft can be restricted and the crankshaft does nothave main-to-rod journal cross-drillings.

Such a reciprocating engine 100 also includes an oil delivery system 150that is configured and arranged so as to provide oil for lubrication tothe cylinder walls 4 as described further herein using an oil spraylubrication regime, and also so as to avoid interference with movableparts of the engine (e.g., crankshaft). In more particular aspects ofthe present invention, such an oil delivery system 150 includes an oilsquirter 152 that is configured so that the oil spraying therefromtargets the cylinder walls 4, but which also does not come into contactwith moving elements of the engine.

In particular embodiments, the oil squirter 152 in each cylinder 2 isconfigured so at least two jets or sprays of oil are provided. The oilsquirter also is arranged within the cylinder so that these sprays orjets of oil target two areas of the cylinder walls. In yet moreparticular embodiments, the oil squirter 152 is configured and arrangedso that a lower portion of the cylinder 2 (e.g., the lower third of thecylinder) in the piston thrust area and the piston anti-thrust area aretargeted by the at least two jets or sprays of oil. In yet furtherembodiments, the oil squirter 152 is fed oil from the cylinder blockprimary oil gallery 130. The direction of these sprays or jets of oilare depicted in FIGS. 3 and 4.

Now with reference also to FIGS. 5-7, each squirter 152 is affixed tothe cylinder block 102, by a fitting 154, which fitting in oneembodiment is a non-regulated bolt 154 a (FIG. 5) as is known to thoseskilled in the art or in another or alternative embodiment, the fittingis an internal pressure regulated bolt 154 b (FIG. 6) as is known tothose skilled in the art. In either embodiment, the fitting 154; 154 a,breceives a flow of oil from the main gallery 130 (FIG. 3) as indicatedin FIGS. 5 and 6. In the case where an internal pressure regulated bolt154 b is used, the oil is delivered to the squirter when the pressure ofthe oil from the main gallery exceeds a predetermined value. In the casewhere a non-regulated bolt 154 a is used, the delivery or flow of oil tothe oil squirter 152 and spraying therefrom can vary due to changingoperating conditions of the reciprocating engine that affect oilpressure.

In further aspects of the present invention, such an oil squirter 152includes a body 160, a first member 162 having two operable ends 163 a,band a second member 164 also having an operable end 165. In particularembodiments, the first and second members 162, 164 are joined to eachother using any of a number of techniques known to those skilled in theart so that the operable ends 163 a, 165 of the first and second membersform nozzles from which the oil is sprayed. Such joining of the firstand second members forms a sub-assembly. The other operable end 163 b ofthe first member 162 is joined to a mating connection or outlet 161 ofthe body 160. In more particular embodiments, the first and secondmembers are tubular metal members. In yet more particular embodiments,the second member 164 is joined to the first member 162 by brazing andthe other operable end 163 b of the first member is joined to the bodyoutlet 161 also by brazing.

In yet further embodiments, the first and second members 162, 164 arejoined to each other so that the operable ends 163 a, 165 of the firstand second members are arranged so as to be at an angle with respect toeach other. In more particular embodiments, the angle is such that oneof the operable ends causes the oil spray or jet to be in the directionof the lower portion of the cylinder 2 (e.g., the lower third of thecylinder) in the piston thrust area and so that the other of theoperable ends causes the oil spray or jet to be in the direction of thelower portion of the cylinder 2 (e.g., the lower third of the cylinder)in the piston anti-thrust area. In an illustrative embodiment, theoperable ends 163, 165 are arranged so as to be essentially orthogonalto each other when the first and second members are joined to eachother. In yet another illustrative embodiment, the angle is 90 deg.±5.

In further embodiments, the first member 162 is configured so that acenterline of the operable end 163 is at an angle to the centerline ofthe other operable end 163 b of the first member that is secured to thebody outlet 161. In an illustrative embodiment, the first member 162includes a bend located between the body outlet 161 and the operable end163 a so that the operable end 163 is at such an angle. The angle isestablished so that the oil squirter 152 is displaced from the movingelements internal to the cylinder block such as the structure formingthe crankshaft 120 and the connecting rod 112.

In further embodiments, the internal structure of at least the operableends 163, 165 of the first and second member 162, 164 are established sothat the oil flowing or spraying from the ends is generally sufficientfor purposes of lubrication. In more particular embodiments, theinternal structure is established so that the flow from each operableend is approximately the same or equalized. In more particularembodiments, the internal structure is established so that the flow fromeach operable end is optimized for the region(s) being targeted.

As the first member 162 is generally less resistive to the flow of theoil as compared to the second member 164, the operable end 163 a of thefirst member is configured so as to increase the resistance to flow suchthat the first member's resistance is about the same as or greater thanthe flow resistance presented by the second member 164 and itsassociated operable end 165. In this way, a more favorable pressuredifferential is established so that the outputs from the two nozzles oroperable ends are at or about a similar value or equalized.

In yet further embodiments and with reference to FIG. 8, the oilsquirter 252 is configured so as to include a proximal member 262 and adistal outlet member 264 having an inlet 263 a connection and twooutlets 263 b,c. One end 263 b of the proximal member 262 is coupled tothe body outlet 161 as described above for the other operable end 163 bof the first member 162 and the other end 263 a of the proximal member262 is coupled to the inlet connection 267 b of the outlet member 264.In this way, oil is fed through the proximal member 262 to the outletmember 264 much the same way as through the first and second members162, 164 so that the oil exits through the outlets 263 b,c and isdirected to the cylinder walls 4 as described herein.

Referring now to FIG. 5, and as indicated above, the illustrated oilsquirter includes a non-regulated bolt 154 a such as a banjo-style boltthat consists of a multiplicity of intersecting cross-drillings toestablish a flow path between the oil flowing from the main gallery tothe body 160. As is known to those skilled in the art, in a banjo-styleof bolt, the oil flows into an internal passage and thence out throughthe cross-drillings to an outer passage that encircles the internalpassage. The oil in the outer passage flows to the body 160.

Referring now to FIG. 6 and as indicated above, the illustrated oilsquirter includes an internal pressure regulated bolt 154 b. In anexemplary illustrative embodiment, such an internal pressure regulatedbolt includes a movable member 170 or piston, a spring member 172 and astop 174. The stop 174 abuts one end of the spring and is connected tothe bolt so that a force acting on the other end of the spring causesthe spring to compress. The movable member 170 abuts the other end ofthe spring 172 such that a force pushing against the movable membertowards the spring causes the spring to compress. In use, the pressureof the oil coming from the main gallery acts on the movable member 170and thus causes compression of the spring 172. In this way, when the oilpressure exceeds a predetermined value, the spring 172 is compressedsufficiently that the movable member 170 moves past the cross-drillingsthereby allowing the oil to flow into the outer passage and thence tothe body 160.

In yet further embodiments, the block of such a reciprocating engine isconfigured so as to include 4 cylinders, 6 cylinders, 8 cylinders, 10cylinders and 12 cylinders, and where the number of pistons correspondsto the number of cylinders. Such cylinders are arranged in thereciprocating engine so as to be inline, slanted, form a V, or arrangedin any of a number of ways as one known to those skilled in the art.

In yet further embodiments, the reciprocating engine is a four-strokeinternal combustion engine or a two-stroke internal combustion engine.

Although a preferred embodiment of the invention has been describedusing specific terms, such description is for illustrative purposesonly, and it is to be understood that changes and variations may be madewithout departing from the spirit or scope of the following claims.

INCORPORATION BY REFERENCE

All patents, published patent applications and other referencesdisclosed herein are hereby expressly incorporated by reference in theirentireties.

EQUIVALENTS

Those skilled in the art will recognize, or be able to ascertain usingno more than routine experimentation, many equivalents of the specificembodiments of the invention described herein. Such equivalents areintended to be encompassed by the following claims.

1. A cylinder wall oil delivery system for a reciprocating engine havingat least one cylinder and at least one piston movably received in thecylinder, said oil delivery system comprising: a squirter that isfixable arranged in a cylinder of a reciprocating engine so that oil isdirected therefrom to two different areas of a cylinder wall; and thesquirter includes a first nozzle that is orientated so that oil isdirected therefrom to one of the two areas of the cylinder wall and thesecond nozzle is orientated so that oil is directed therefrom to theother of the two areas of the cylinder wall.
 2. The cylinder wall oildelivery system of claim 1, wherein oil from the squirter providescooling by oil spray wash-up.
 3. The cylinder wall oil delivery systemof claim 2, wherein oil wash-down of the oil sprayed from the squirterfurther causes lubricant to be splashed onto the connecting rodbearings.
 4. The cylinder wall oil delivery system of claim 1, whereinthe squirter is arranged in the cylinder so that the oil spray/jettargets a region of the cylinder wall corresponding to a piston skirtthrust travel area and a piston anti-thrust travel area.
 5. The cylinderwall oil delivery system of claim 1, wherein the squirter includes asub-assembly including a first member and a second member that arejoined together so as to form the first and second nozzles and whereinthe first and second members are configured so as to regulate the flowfrom each nozzle.
 6. The cylinder wall oil delivery system of claim 5,wherein the first and second members are further configured so that theflow from each nozzle lies within a range of desired values.
 7. Thecylinder wall oil deliver system of claim 1, further comprising apressure regulator fluidly coupled to the squirter so that oil isdelivered to the squirter when pressure of the oil exceeds apredetermine value.
 8. A reciprocating engine comprising: a block havingat least one cylinder therein; at least one piston, each of the at leastone piston being movably received in the at least one cylinder; asquirter that is fixably arranged in each of the at least one cylinderso that oil is directed therefrom to two different areas of the cylinderwall; and wherein the squirter includes a first nozzle that isorientated so that oil is directed therefrom to one of the two areas ofthe cylinder wall and the second nozzle is orientated so that oil isdirected therefrom to the other of the two areas of the cylinder wall.9. The reciprocating engine of claim 8, wherein the squirter is arrangedin the cylinder so the oil spray/jet targets a region of the cylinderwall corresponding to a piston skirt thrust travel area and a pistonanti-thrust travel area.
 10. The reciprocating engine of claim 8,wherein the squirter includes a sub-assembly including a first memberand a second member that are joined together so as to form the first andsecond nozzles and wherein the first and second members are configuredso as to regulate the flow from each nozzle.
 11. The reciprocatingengine of claim 5, wherein the first and second members are furtherconfigured so that the flow from each nozzle lies within a range ofdesired values.
 12. The reciprocating engine of claim 1, furthercomprising a pressure regulator operably coupled to the squirter so thatoil is delivered to the squirter when pressure of the oil exceeds apredetermined value.
 13. The reciprocating engine of claim 8, whereinthe block further includes a number of cylinders selected from the groupconsisting of 4 cylinders, 6 cylinders, 8 cylinders, 10 cylinders and 12cylinders and a number of pistons that corresponds to said number ofcylinders.
 14. The reciprocating engine of claim 8, wherein thereciprocating engine is a four-stroke internal combustion engine. 15.The reciprocating engine of claim 8, wherein the reciprocating engine isa two-stroke internal combustion engine.
 16. The reciprocating engine ofclaim 8, further comprising: a crankshaft; at least one connecting rodoperably coupled to said at least one piston and the crankshaft suchthat linear motion of the at least one piston in the at least onecylinder causes rotation of the crankshaft; and a rolling elementbearing rotatably supporting the crankshaft.
 17. The reciprocatingengine of claim 16, further comprising: a second rolling element bearingthat rotatably supports an end of the connecting rod from thecrankshaft.